Compensating high-duty pumping-engine.



G. DE LAVAL 8'. G. P. ABURN.

Patented Ian. l4, I902.

COMPENSATING HIGH DUTY PUMPING ENGINE.

(No Model.)

(Application filed July 27, 1900.)

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Patented Jan. I4, I902.

6. DE L I-\VAL & G. P. ABORN.

COMPENSATING HIGH DUTY PUMPING ENGINE.

(Application filed Ju1y27, 1800.)

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(No Model.)

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G. DE LAVAL & G. P. ABDRN.

CDMPENSATING HIGH DUTY PUMPING ENGINE.

(Application filed July 27, 1900.

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No. 690,969. Patented Jan. [4,, 1902.

G. DE LAVAL &. G. P. ABURN.

CUMPENSATING HIGH DUTY PUMPING ENGINE.

(Application filed July 27, 1900.)

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GEORGE DE LAVAL, OF CAMBRIDGE, AND GEORGE P. ABORN, OF BOSTON,

MASSACHUSETTS.

COMPENSATHNG HBGH DUTY PUMPINC EI-INGINE.

SPEKJIFXOATI ON forming part of Letters Patent NO. 690,969, dated January 14:, 1902.

Application filed July 27, 1900. Serial No. 24,991. (No modeL) To all whom it may concern:

Be it known that we, GEORGE on LAVAL, a resident of Cambridge, county of Middlesex, and GEORGE P. ABORN, a resident of Boston,

county of Suffolk, Commonwealth of Massachusetts, citizens of the United States, have invented an Improvement in Compensating High-Duty Pumping-Engines, of which the following description, in connection with the KO accompanying drawings, is a specification, like characters on the drawings representing like parts.

This invention relates to duplex pumpingengines wherein the pump is direct acting I5 and the steam is used expansively, resulting in a simple, economical, and efficient apparatus. In such engines various devices have been employed to distribute the power exerted by making use of compensating mechanism,

so that when steam-admission ceases and the driving forces diminish said mechanism transmits the force in excess from the opposite engine to enable the first to complete the stroke.

In United States Patent No. 520,237, dated May 22, 1894, an auxiliary cylinder is employed containing a piston acted upon by fluid-pressure and forming part of the compensating mechanism, the power of this cylinder acting through varying leverage to absorb the excessive energy during the early part of the stroke and in like manner to give out the excessive energy during the last part of the stroke when the steam-admission to the main engine has ceased. In a later patcut, No. $2,081, three pumps are connected by a revolving shaft which receives its motion from connections to the compensating levers, providing for a regularity of action in the three engines, the'construction therein 40 shown being particularly adapted to compound engines.

Our present invention is adapted more particularly to compound direct-acting pumping-engines, and we have greatly simplified 5 the construction of the compensating mechanism, obviating the use of fly-wheels, auxiliary compensating pressure-cy1inders, aocumulators, and a large number of steam-cylinders, the compensating mechanism, hereinafter to be described, acting very directly to transmit the excessive force of the steam before cut-off in one steam-cylinder to the piston of another cylinder in which the steam is acting expansively, this invention being equally adaptable to the various forms of engines using steam expansively, to be described.

The compensating mechanism embodying our invention can be constructed in a number of different forms, according to the general arrangement and scope of the engine with which it is combined, and we have herein shown in detail several ofsnch forms, and in addition we have illustrated diagrammatically other forms in which the compensating mechanism may be embodied.

Figure 1 is a front elevation of the main portion of a triple-expansion high-duty pumping-engine embodying one form of our invention, the valve mechanism, which may be of any usual construction, being omitted for the sake of clearness and as forming no part of our invention. Fig. 2 is a similar view of a high duty cross compound doubleacting pump with another form of our invention embodied therein. Fig. 3 is a section thereof on the line a: a, Fig. 2, as seen from above. Figs. 4, 5, 6, and 7 are diagrammatic views of the engine shown in Fig. 1, only two steamcylinders being represented, however, to sim- 8o plify the drawings, the pistons being shown at different parts of their stroke. Figs. 8, 9, 10, and 11 are similar views of the engine shown in Fig. 2 to illustrate the operation of the compensating mechanism. Figs. 12 to 25, inclusive, are diagrammatic views showing various modified forms of compensating mechanism,Fig. 23 corresponding to the structure illustrated in detail in Fig. 1.

Referring now more particularly to Fig. 1, go a triple-expansion vertical engine is shown, the high, low, and intermediate pressure steam-cylinders being indicated herein, as elsewhere in the drawings, as HP, LP, and IP, respectively, the pistons being shown by 5 dotted lines. The pumps P P are directly actuated by the piston-rods h Z and a crossgirth A of the engine -frame between the steam-cylinder pedestals A A is provided with a guideway a for a reciprocating member or too cross-head T, through which power is transmitted to the opposite engine, said member acting in compression. The piston-rods are provided, respectively, with cross-heads 72 Z, sliding in vertical guideways in usual man- Compensating levers H L are pivotally connected at their outer ends to the piston-rod cross-heads, said ends preferably having a sliding movement in the latter, as by blocks 300 400, sliding for a limited distance laterally in the cross-heads, the inner ends of the levers being pivotally connected to the member '1, which latter, being guided in the guideway a forms a support for the compensating member and also a connection between said levers, the latter being of such length that when one piston is at half-stroke its corresponding lever will be substantially horizontal in the construction illustrated, while the other lever will be inclined, as shown. A swinging radius-bar h, pivoted at its outer end on the pedestal A, is pivotally connected at its inner end to the lever H forming a swinging fulcrum support therefor, and a similar radius-bar Z is pivotally connected to the lever L and to the pedestal A.

In the compensating mechanism described the fixed points 30 40, about which the radiusbars swing, are located between the pistonrods, and it will be noted that the piston-rods and compensating levers, as well as the levers and radius-bars, form toggles. Nhen a piston is at half-stroke, its connected compensating lever and compensating radius-bar will be substantially horizontal, thelever and radius-bar at the other side of the engine being inclined above or below a line through the axes of the levers, according to the direction of movement of the cooperating pistonrod. As the inclined lever approaches the horizontal position the other lever forms a gradually increasing angle with the line through the axes of said levers, the compression memberT moving toward that side which is receiving assistance, .and this transmitted force continues to act until the piston of that side from which it is transmitted reaches midstroke. Thereafter the conditions are reversed, and the side of the engine which had received aid now operates through the compensating mechanism to assist the other side.

In Fig. l the high and intermediate pistons are just about to begin the upward stroke with full steanrpressure, and the low-pressure piston is in mid-position on the downward stroke, cutting off having taken place, and the aid of the other side of the engine is required to effect completion of the downward stroke by transmitting some of the surplus force at the left-hand side of the engine. As the piston-rod h moves upward the toggles h H and h 11 gradually straighten, the approach of the compensating lever IP to horizontal position acting to force the member T to the right,this force being transmitted through the lever L in a downward direction to the piston-rod Z as it completes its downward stroke, the lever L swinging on the radiusbar I" as the inner end of the latter moves downward. The complete cycle is shown in Figs. at to 7, inclusive, the direction of movement of the pistons being indicated by arrows.

In Fig. 4 the high and intermediate pressure pistons have just completed their upward stroke and are starting downward, while the low-pressure piston is moving upward, having completed the first half of the stroke. The left-hand side of the engine being at the commencement of its stroke has an excess of steam-pressure, and this is resisted by the force which it transmits through the compensating levers H L to the right-hand side of the engine, thereby preventing any hesitating or uncertainty of the piston-rod Z as it finishes its upward stroke, the completion of the stroke being definite and steady.

In Fig. 5 the right-hand side of the engine is under its full steam-pressure, downward stroke just'beginning, while the steam has been cut off in the lett-hand side at substantially half-stroke and the excess or unnecessary power of the right-hand side of the engine is transmitted through the compensating mechanism to the left-hand piston to assist the piston-rod in completing its downward stroke while its steam acts expansively.

In Fig. 6 the right-hand side is about to be assisted to complete its downward stroke, and in Fig. 7 the right-hand side is about to assist the left-hand side of the engine to finish its upward stroke, completing the cycle. The single cylinder shown at the left-hand side of the engine in these figures is indicated for convenience by the letters HP, that being the side of the engine 011' which the HP and IP steam-cylinders are located in the type of engine illustrated.

The direction of movement of the radiusbars in Figs. 4 to 7, inclusive, is indicated by the arrows 3 and 4. During the first part of the stroke the surplus power developed by the high and intermediate cylinders is transmitted by the compensating means to assist the low-pressure cylinder during the latter part of each stroke, the low-pressure cylinder in turn during the first half of its stroke assisting the high-pressure side while it is completing a stroke. There is no dead-center with this compensating mechanism, and the transmission of power from one to the other side of the engine is direct and effective. The member T moves in a fixed path at right angles to the stroke of the engine and is under compression, as will be manifest from the foregoing description and from an inspection of the various diagrammatic views in the drawings, the said member constituting a supporting member or device for the compensating mechanism. The levers II L are each composed of parallel plates which straddle the cross-heads on the piston-rods. The member T and the radiusbars h Z are also arranged in parallel parts.

Referring to Fig. 2, a cross-compound engine is shown, the compensating mechanism being embodied in a different form, the connection with the piston-rods b o of the HP and LP steam-cylinders being made in usual manner. Pillars 6, 7, and 8 rigidly support the steam-cylinders, (see also Fig. 3,) brackets B and 0 being secured to the pairs of pillars 6 8, respectively, outside of the pistonrods, and to these brackets are pivoted at 50 and pairs of radius-bars b a, respectively. The pairs ofradius-bars straddle their respective piston-rods and extend inward beyond them and receive between them compensating levers B (3 pivotally connected at 51 and 61 to the radius-bars. The levers are made up of pairs of parallel plates, (see Fig. 3,) each pair of plates constituting a lever and being pivotally connected with a piston-rod by means of the collars B O thereon. The inner ends of the compensating levers are pivotally connected with a cross-head T which forms the compression member of the compensating mechanism, said member being mounted to slide laterally in a guide 70, formed in a horizontal cross-girth B ,extended between the pillars 7, the ends of the girth being further braced by tie-rods 72, secured to the brackets B C. The high-pressure piston is on the upward stroke, the steam acting expansively, andthe low-pressure pistonis on the downward stroke, steam still being admitted to its cylinder, and as the toggle 0 0 is straightened the power in excess will be transmitted through the member T to the piston-rod b to assist its engine in the completion of its upward stroke. The complete cycle is shown diagrammatically in Figs. 8 to 11, inclusive, the

surplus power on the high-pressure side in Fig. 8 assisting the low-pressure piston to complete its downward stroke, while in Fig. 10 the assistance is being given to complete the upward stroke of the low-pressure piston.

In Figs. 9 and 11 the low-pressure cylinder at the beginning of its stroke is assisting the high-pressure piston to complete its downward and upward strokes, respectively, the operation of the compensating mechanism being clearly illustrated. The fixed fulcra of the radius-bars in this form of the compensating mechanism are located outside of the piston-rods, the said bars swinging inward, the operation thereof being similar in its toggle action and in other features to the construction heretofore described.

A number of modified forms of the compensating mechanism embodying our invention are shown diagrammatically in Figs. 12 to 25, inclusive, and these are divided into two series, the even-numbered figures showing a sliding power-transmitting member T movable in a fixed path by means of a guide g, while in the odd-numbered figures the compensating levers are connected at their inner ends without the intervention of a cross-head or sliding member, and the connection moves in a direction transverse to the piston-stroke. A radiusarin R is substituted for the guide g, causing the connection to move in a fixed but slightly curved path, said radius-arm constituting a supporting device for the mechanism. In these views the high and low pressure cylinders are indicated by the letters Hp and Lp, respectively, as before, their pistons by the letters m 'n the compensating levers by M N respectively, and the radius-bars by the letters m n.

The form shown in Fig. 12 is very simple, the levers M N being connected at their inner ends to the member T and at their outer ends to the cross-heads m n on the pistonrods, said cross-heads traveling in vertical guides m 17. respectively. By connecting the compensating levers directly at their inner ends, as at 12, Fig. 13, the sliding member T is omitted, but the radius-arm R. is employed, jointed at 12 to the levers and swinging about a fixed fulcrum.

In Figs. 14 and 15 an outside connection is shown, the radius-bars being fulcrumed at 81 and at their inner ends jointed to the levers M N short links 82 83 connecting the joints with the piston-rods, the crosshead T and its guide 9 being shown in Fig. 14 and the swinging radius-arm R in Fig. 15 in lieu thereof, fulcrumed at 13.

Other compensating mechanisms are illustrated in Figs. 16 and 17 with the member T and the radius-arm R, respectively, short links 84: 85 connecting the compensating levers with the piston-rods, it being noted that the links are not connected to the joint between the levers M N and the radius-bars, which latter are in these figures considerably longer than the levers.

In Figs. 18 and 19 the compensating levers are longer than the radius-bars and directly connected to the piston-rods,while the radiusbars are jointed to the lever at substantially their centers at 86 and 87, the radius-bars n coinciding with the position of the levers N in the positions illustrated, and the fixed pivots 88 89 of said bars are substantially in alinement with the piston-rods. In the instances where the radius-arm R is used the are through which its free end swings is short IIO &

in those figures omitted, as they may be by careful construction and relative arrangement of parts.

The construction shown in Fig. 22 is substantially that shown in Figs. 2, 8, 9, 10, and 11, and the same is true of Fig. 23, except that the radius-arm R is used, jointed at 12 to the connected inner ends of the compensating levers M N A different arrangement of the parts is shown in Figs. 24 and 25, the radius-bars being fulcrumed at 94 95 beyond the pistonrods and connected therewith at their inner ends by short links 92 93, while the outer ends of the compensating levers are pivotally connected at 96 97, respectively, to the radiusbars between their ends.

In all of the modifications herein shown the same underlying principles of our invention are embodied, the excessive pressure at the beginning of the stroke of one side of the engine being transmitted to the other side, where the force is inadequate to assist the piston or pistons at that side in completing the stroke.

While we have herein shown our compensating device as applied to a multiple-expansion engine used in connection with the direct-acting pump, yet it will be obvious that the same compensating mechanism could be used in connection with two cylinders taking steam at the same pressure rather than at different pressures.

Our invention is not restricted to the particular forms of compensating mechanism herein shown, as it will be manifest from the various modifications herein illustrated that the compensating mechanism may be constructed in a number of different forms without departing from the spirit and scope of the invention.

Having fully described our invention, what We claim as new, and desire to secure by Letters Patent, is-- 1. Inahigh-dutypumping-engine, a directacting pump, a pair of steam-cylinders and their pistons, to actuate the pump, mechanism constituting with the piston-rods compensating toggles, a movable support intermediate and operatively connected with the toggles, and means to guide said support in a path substantially perpendicular to the piston-rods.

2. In ahigh-duty pumping-engine, a directacting pump, high and low pressure steamcylinders and their pistons and their rods, to actuate the pump, a reciprocating powertransmitting member between and movable substantially at right angles to the piston rods, compensating mechanism between the latter and said member and pivotally connected with each, and means to guide said member in a fixed path.

3. Inahigh-dutypumping-engine,adirectacting pump, high and low pressure steamcylinders and their pistons, to actuate the pump, compensating mechanism comprising two sets of toggles operatively connected with the piston-rods of said pistons, a coupling member pivotally connected with the toggles, and means located between the piston-rods to guide the coupling member in a fixed path of movement.

4. The combination with a duplex directacting pump, and high and low pressure steam-cylinders and their moving pistons, of compensating mechanism operatively connecting the piston-rods of said pistons, said mechanism including a transmitting member movable in a fixed path substantially at right angles to the stroke.

5. The combination with a duplex directacting pump, and high and low pressure steam-cylinders and their pistons, of compensating mechanism operatively connecting the piston-rods of said pistons, said mechanism including two oppositely-acting toggle devices connected respectively with the pistonrods, and a connecting member between the toggles and means independent from the toggle to guide said connecting member in a fixed path substantially at right angles to the stroke.

6. The combination with a duplex directacting pump, and high and low pressure steam-cylinders and their pistons, of compensating mechanism,operatively connecting the piston-rods of said pistons, said mechanism including two oppositely-acting toggles connected respectively with the piston-rods, a fixed fulcrum for a member of each toggle, a common power-transmitting member pivotally connected with the toggles, and means independent of the toggles to guide the transmitting member.

7. The combination with a duplex directacting pump, and high and low pressure steam-cylinders and their pistons, of two levers, pivotal connections between their outer ends and the piston-rods of said pistons, a connecting member, to which the inner ends of the levers are pivotally attached, swinging supports on which the levers are fulcrumed, and means independent from the levers to guide said connecting member in a fixed path substantially at right angles to the stroke.

8. The combination with a duplex directacting pump, and high and low pressure steam-cylinders and their pistons, of two levers, pivotal connections between their outer ends and the piston-rods of said pistons, a connecting member between the latter, to which the inner ends of the levers are pivotally attached, swinging supports on which the levers are fulcrumed, and meansindependent from the levers to guide the connecting mem her in a fixed path of movement between the piston-rods, whereby a force is transmitted from one side to the other through different portions of the stroke, to assist the other of said pistons.

9. The combination, in a compound direct- IIC acting pnmpingwngine, of a plurality of guide for said compression member indesteam cylinders taking steam at difiierent pendent from the levers.

pressures, their reciprocating pistons, and a In testimony whereof We have signed our pump actuated thereby, of compensating names to this specification in the presence of 15 5 mechanism between and connecting the pistwo subscribing Witnesses.

ton-rods of said pistons, to bring into operation a force to assist the movement of the {3 other piston, said compensating mechanism K including a power-transmitting compression Witnesses: IO member reciprocating in a fixed path sub- JULIUS MEYERS,

stantialiy at right angles to the stroke, and JOHN J. FINLEY. 

